Record controlled accounting machine



March 16, 1948. T. J. WATSON rs1-Al.` 2,438,081

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March 16, 1948. T. J. WATSON Erm.

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INVENTORS March 16, 1948. T. J. WATSON ETAL. 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July 15, 1943 17 sheets-sheet 4 March 16, 194s.

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RECORD CONTROLLED ACCOUNTING .MACHINE Filed July 15, 1945 1'7 sheets-sheet 7 y INVENTORS THMAS Il. WATSON 'Minas s. sa rr/r FRIDE TTORNE Y T. J. WATSON ETAL RECORD CONTROLLEDKACCOUNTING MACHINE March 16, 1948.

Filed July l5, 1943 1'7 Sheets-Sheet 8 IN VENT ORS March` 16, 1948. T WATSON TAL 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July l5, 1943 17 Sheets-Sheet 9 F le. 10.

ATTORNEY March 16,1948. T. .L wA'rsoN x-:TAL 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July l5, 1943 17 Sheets-Sheet l0 March 16, 1948. 1 WATSON ET AL 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July 15, 1943 17 Sheets-Sheet l1 FIG-M2.

IN VEN TORS M ATTORNEY.

l March 16, 1948.

T. J.'WATSON ETAL.

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Exe-'carers ATTORNEY.

T. J. WATSON Er AL 2,438,081

RECORD GONTROLLED ACCOUNTING MACHINE Filed July l5, 1943 '17 Sheets-Sheet l5 March 16, 1948.

IN VEN TORS A ITORNEY.

March 16, 1948. T. J. WATSON ErAL 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July 15, 194s 17 sheets-sheet 14 March 16, 1948. T. J. WATSON ETAL RECORD CONTROLLED ACCOUNTING MACHINE Filed July `15, 1943 17 Sheets-Sheet l5 IN VEN TORS d. v4 rsa# ATTORNEY March 16, 1948. T. J. WATSON ETAL.

RECORD CONTROLLED ACCOUNTING MACHINE Filed July l5, 1943 17 Sheets-Sheet 16 March 16, 1948.

T. 1. WATsoN Erm. 2,438,081

RECORD CONTROLLED ACCOUNTING MACHINE Filed July l5, 1943 17 Sheets-Sheet 17 IN VENT ORS' A TT ORNE Y Patented Mar. 16, 1948 RECQRD CON TROLLED ACCOUNTING MACHINE Thomas J. Watson,

New Canaan,

Conn., Horace S. Beattie, East Orange, N. J., and Frederick L. Fuller, deceased, late of West Orange, N. J., vby

Schuyler B. Harrison, East Orange, N. J., and l.lohn G. Phillips, New York, N. Y., executors,

Corporation, New York Application July 15,

This invention relates to accounting machines and more particularly to the type for `its main object the construction of a record controlled accounting machine which will carry out the functions required of a commercial machine by constructions which operate in a more eiiicient and novel manne-r. The constructions are devised particularly with the viewpoint of deriving the increased ciciency by adopting constructions which render available an increase in speed of accounting and .at the same time insure accuracy in accounting and printing functions.

The present invention has for its object the coordination of an item accumulating mechanism with the record controlled alphabetic-numeric rotary printing mechanism shown in the patent to Fuller et al. No. 2,199,561 whereby in credit items, listing of such items, and related totals, either as positive or negative balances, all of which functions are a cardinal requirement of modern commercial tabulating machines.

Of course, without accuracy in accounting operations such forms of machines would have no commercial value and the present accumulating functions insuring accurate accumulating operations by adopting constructions which are less likely to require service to insure continuous high speed accurate accounting operations.

One rigid requirement of all accounting machines is the requirement that correspondence be secured between the digit entered in an accumulator and printed and in the present arrangement the clutch which is engaged under record `perforation control to initiate the setting of the printing element has a positive mechanical connection to the control member which determines the initiation or termination ofthe operation of the accumulating element, depending upon the type of entry to be effected.

Another object of the invention relates to the accumulating mechanism and its Vaddition and subtraction control whereby a single accumulator receives additive and subtractive entries to arrive at a balance. Such controls operate in a facile and efficient manner, simplifying those previously devised and by their execution correct additive and subtractive entries are insured.

Another object i the invention relates tothe total printing mechanism which normally yprints the credit amounts amounts and to Business Machines Y., a corporation vof 1943, Serial No. 494,820 31 Claims. (Cl. 235-618) the negative lcredit balance as a Ltrue number by the total printing mechanism.

the drawings:

Fig. 1 is a .front elevational view of the improved tabulating `machine with .section lines ai plied to vindicate 'where the different sectional views of theidrawngs are taken.

Fig. la is an outline of a typical .computation involving bot-h debit and credit balances.

Fig. 2 is a sectional View taken 2`2 of Fig. .l at the left end ofthe tabulating showing the `preferred yform of card feeding mechanism tor the machine.

Fig. 3 is a sectional view taken Aon the line 3-3 of Fig. l, showing particularly the driving mechanism for the card .feeding rollersandstacking mechanism.

Fig. 1, showing particularly the operating mechanism for certain devices associated with Athe :accumulator section ofthe machine Fig. 6 is a detail view showing the outline of a set of complementary cams.

Fig. '7 similarly is a detail view, showing the outline of other complementary driving cams of the machine.

Fig. 8 is a sectional view taken on the irregular section line 3-3 of Fig. l, showing some of the operating mechanism associated with the printing section of the machine.

Fig. 9 is an end view taken near the right hand end of the machine and is taken on the line 9-3 of Fig. 1. This view shows the inter-related gearing mechanism for driving the main operating shafts of the machine.

Fig. 10 is a front elevational view taken on the line i-iii of Fig. 4.

Fig. 11 is a front elevational view taken on the line Ii-ll of Fig. 4a.

Fig. 12 is a front elevational view of the gear driving and variable gear transmission mechanism.

Fig. 13 is a sectional view taken on the line ia-na of Fig. 12.

'Fig 14 is a longitudinal sectional view of the variable gear transmission mechanism.

Fig. 15 is a transverse sectional view, showing a preferred form of restraining mechanism of the frictional type utilized to improve the operation of the variable gear transmission mechanism.

Fig. 16 is a detail view, showing one of the operating cams of the machine and associated follower arm.

Fig. 17 is a timing diagram. particularly for the mechanically operated parts of the machine..

Fig. 18 is a timing diagram of the cam operated contacts and other impulse emitters.

Fig. 19a and Fig. 19o when arranged together in such order comprise the wiring diagram of the machine.

Driving mechanism The driving mechanism for the tabulating machine is best shown in Figs. 9 and 12 wherein it will be seen that i3 represents a constantly rotating shaft of the machine which is driven by an electric motor, theA latter constantly running for successive operations of the tabulating machine. To the shaft lil there is secured a gear l l meshing with a gear l2 secured to a shaft I3. The gear l2 meshes with a gear Li which is pinned to a shaft l5 and also secured to the shaft l5 is a gear i3 which is also shown in Fig. 14. Gears ld and i3 rotate simultaneously with the shaft l5 to which they are pinned. The gear i3 through a pinion 34 (Figs. 9, l2) drives a shaft 33 and shaft 35 is the printer drive shaft which rotates with a uniform speed of rotation. Reference numeral i1 designates the other printer drive shaft which rotates with a uniform speed of rotation substantially synchronously with the drive shaft 35 but at times the speed of rotation given to shaft i1 is decreased with respect to the drive shaft 33 for a purpose'to be more clearly understood later on. The variable drive for driving shaft i1 at the desired speed will now be described in detail: This mechanism is best shown in Figs. l2, 13 and 14. Pivoted by a stud i3 on the outer periphery of the gear i3 is an arm I3 and said arm carries a cross member in the form 'of a stud 23 which extends to the left as shown in Fig. 14 and is also carried by an arm 2l (Fig. 14) which is pivoted by a screw stud 22 on the gear i4. The screw studs i3 and 22 are always co-axial because they are pivoted on gears lil and i3 which rotate simultaneously. The arm 2l carries a roller 23 which engages the cam race 24 of a plate 23 which is K member 2i attached by screws `Z3 (Fig. 13) to a side frame The cam race 23 is so designed that the yoke comprising the two side arms i9 and 2l and the cross stud 23 may be rocked about the studs i3 and 23 and since the stud 20 passes through the gear iii, as shown in Fig. 14, the latter is cut out as shown by reference numeral 28 in Fig. 13 to permit this independent rocking movement of the yoke. The stud 22 also extends to the right through the gear i4 as shown in Fig. 14 to receive a fork 23 of an arm 33 through which also passes the cross rod 2li. The arm 33 is also forked at 3i (see Fig. 13) to receive a stud 32 carried by a gear 33. The gear 33 is carried by a sleeve 3l, the latter being` mounted on the shaft l5 by ball bearing assemblies. The gear 33 through a pinion 38 drives the printer drive shaft i1 which is to be known as the variably driven printer drive shaft of the machine. With the parts at normal as shown in Fig. 13, gears ist and i3 rotate in a clockwise direction, and the roller 23 will cooperate with a substantially concentric portion of the cam race 24 and since there will be no rocking of the arm 33 at this time, its connection to the gear 33 by engagement with the stud 32 carried thereby will cause the gear 33 to be given a rotation in a clockwise direction at substantially the same speed as the gears lli and i3. This occurs from 0 to 171 during which time the 9-1 index point positions are successively analyzed by the analyzing brushes. When the roller 23 strikes a cam portion designated 24a (Fig. i3), which occurs 0, X, and R index point positions are analyzed, the yoke is rocked by rod 2o counterclockwise about the pivot stud zfrocking the arm 33 in the same direction, thus rotating the gear 33 counterclockwise or backwardly with respect to the rotation of gears i4 and I3. Gear 33 is cut out at 23' (Fig. 13) to enable this backward rotation without being interfered by stud 23 which passes through the slot 23' of gear 33. This will result in diminishing the speed of rotation of the gear 33 and shaft i1 during the analysis of the 0, X and R index point positions. After the reduction in speed of the gear 33 the roller 23 then enters the cam portion 24D (Fig. 13) and the latter is so designed as to rock the arm 33 clockwise and so fast that it will cause the gear 33 to rotate at a speed increased with respect to the gears i3 and i3. This increase in speed ensues during the latter portion of the machine cycle to make up for the previous relative displacement of gear 33 so that at the beginning of the next cycle the gears ll-i3 and 33 are at their relative normal position.

It has been found in practice that the abrupt change in speed from the uniform speed of rotation of the shaft i'i to a lower speed of rotation has caused a whipping cf the variably driven shaft il, causing a strain upon this shaft as well as the parts operated thereby. To this end it is desirable to frictionally drive the shaft l1 by the following preferred means. The shaft 33 which is driven at the uniform speed of rotation has secured thereto at its right end a pinion lil (Figs. 9 and l2) which meshes with a gear lil. The gear (il, it will be observed from Fig. 15, is secured in any suitable manner to a sleeve E loosely mounted upon a stud @.3 which is screwed in the side frame member lili. The sleeve 32 also has secured thereto in any suitable manner a conically shaped clutch member (l5. This constitutes the driving clutch member driven by the gear lil and the other or driven clutch member consists of an annular shaped member 41 loosely mounted on the stud and which carries a clutch facing it shaped at its periphery to pro vide a contour complementary to that oi the driving clutch member The driven clutch ember fl'i is provided with gear teeth around its periphery and said gear teeth mesh as shown in Fig. 9 with a gear til (see Fig. i2) pinned to the shaft il. A spring (see 15) encircling stud 6.13 urges the driving clutch member i5 against the driven clutch member ill, such action being controlled by the cam lace formed on an annular cam ring integral with the gear lili. A U-shaped plate u which is attached to the ide frame member so as to be stationary carries rollers cooperating with the cam rihe cam is so designed that a separation is effected between the clutch ele.. ents and until at about 187 of the machine cycle at which time the rollers d will cooperate with a lower portion ol the cam enabling the spring El to force the clutch member (i5 against the driven clutch member thereby effecting a friction-.el drive from the shaft 35 to the shaft l l, this being maintained by the can: i* from 187 to 255 oi the machine cycle (see Fg. i?) during which time the (l, X and R index point positions are being analyzed on the card.

Referring to Fig l the countercloclcwise trectl shaft is driven a at a uniform speed oi rotation and by moans or variable speed drive, shaft il is being rotated the same direction but at a reduced speed between 187 and 255 oi' the machine' cycle. During this time the iriction drive operates to drive the shaft il .e shaft in the same direction and this friction drive cooperation with the variable speed drive enables the latter to reduce the speed the shaft i l gradually Without any abruptnees in change in speed. f course, while the shaft drives the shaft il through the friction drive its speed is by the variable speed drive, a certain amount oi slipping being efected between the clutch elements and lill so that shaft il is driven only at ti e speed'deterinined by the variable speed drive.

Alphabet mechanism The machine is preferably provide. with alphabet character printing type and means for selecting such type so as to print, aside from numerals, letters making up Words or abbreviations.

The printing mechanism shown herein is generally similar to that fully shown and described in the patent to L. Fuller and H. S. Beattie, No. 2,l9,56i, dated Ii/iay 7, 194i).

The alphabet type are selected by perforations arranged according to the code shown in Fig. lib. The particular o, X and R perforation appearing in a column determines which of the several type oi a group related to an index point Will be printed. For example, if the perforation should be at the 2 hole and no pilot hole is utilized in either the X or R positions, the digit 2 will be r a hole is also at 0 the 0 hole will select the type S; if at the X index point position, type K will be selected and if at the R position, type B will be selected.

Each index point position selects a group of three alphabet type (except the l hole) and also a numeral type. As will be later described, ii a numeral type is to b-e selected for printing, the printing impressions will be taken at the il the machine cycle, which point is after point position is analyzed. (See Fig. 1'7, timing for Machine impulses.) The alphabet type selection is provided for by taking print ingimpressions before the time a numeral type would have been printed and this is eiected under control of the 0, X and R index point positions.

lr" the hole is at the 9 index point position alone, the printing wheel Gil (Fig. 4) will be rotated counterclockwise until the 9 type is at the printing line and then the printing Wheel da will rocked to effect the printing impression. It w li be noted 'that if a perforation is also at the R position, then under control of this perforation the printing wheel will be rocked earlier than for printing the digit 9 to take an imprint from the i type. The perforation at the X position will rock the pri ng Wheel 69 to take an imprint still earlier to print R and the perforation at the 0 position even still earlier to print Z.

The same principle of operation is provided for selecting the type of the other groups of alphabet type and the operation of the printing mechanism for eiecting type selection and printing impressions will now be described in detail:

The card is perforated with holes to represent the digits @-9 and is passed by analyzing brushes by a card feeding mechanism which will be sube sequently described in detail to analyze the index points in the order 9, 8, '7 X and R.

When the analyzing brush senses a hole at any oi the index point positions 9 1, a circuit is closed to a printing control magnet (Fig. Il) and for each card column analyzed there is a printing control magnet Si. When a printing control magnet di is energized its armature 62 is attracted so as to pull a call Wire 63 which rocks a bell crank it. Pivoted to the bell crank 5t is a T-shaped member and its head portion is provided With projections GER and del., the extension GSR normally engeging an extension of a clutch release arm The engagement of extension SSR and the clutch release arm t? is retained in the relationship shown in Fig, Li during the time the holes 9, 8, '7, 6, 5, 4, 3, 2 and l are analyzed to thereby cause the clutch release arm S? to be rocked at a differential time when magnet i is energized.

Shaft il, which it will be recalled, is driven at a variable speed but driven at a uniform speed during the time the index point positions 9-l are analyzed, has secured thereto a tube 58 which' is uted transversely along its periphery so as to provide clutch notches 69. Tube GS constitutes the driving clutch member. Encircling the clutch tube {il} is a plurality of gears itl, there being one gear 'Iii for each order of the printing mechanism. To provide for the lateral spacing between the gears 'lil the gears are guided by slots Well as by guide slots i4 in a casting l5. By such spacing members the gears 'iii are separated to allow independent movement and also to cause a clutch pawl 'l which is pivoted on the related gear 'iii to cooperate With the clutch release arm G'l. The clutch release arm 6l normally holds the clutch When the e arm el is rocked as a result of the energization of the magnet 6l, the clutch is engaged because a spring it attached to the clutch paWl i6 will rock the Alatter in order that the clutch tooth 'l will engage the clutch notch 9 determined by the time the printing control magnet tl is energized. The above described clutch is the printing type selecting clutch and causes the diiierential rotation of the printing 

